JP2018013152A - Torque fluctuation suppression device, torque converter, and power transmission device - Google Patents

Abstract

PROBLEM TO BE SOLVED: To suppress peak of torque fluctuation in a wide rotating speed range, in a device for suppressing torque fluctuation of a rotary member.SOLUTION: A device includes an inertia ring 20, a centrifugal element 21, and a cam mechanism 22. The inertia ring 20 is disposed while axially arranged in line with an output-side rotor 12, and rotatable to the output-side rotor 12. The cam mechanism 22 has a cam 31 and a roller 30, and receives centrifugal force acting on the centrifugal element 21 to convert the centrifugal force into the circumferential force in a direction to reduce rotational phase difference, when the rotational phase difference is generated between the output-side rotor 12 and the inertia ring 20. Guide rollers 26a, 26b are disposed at both end portions of the centrifugal element 21. The guide rollers 26a, 26b are kept into contact with a projecting portion 121 of the output-side rotor 12 at a position at the side opposite to a contact point of the cam 31 and the roller 30 through the center of gravity of the centrifugal element 21.SELECTED DRAWING: Figure 4

Description

  The present invention relates to a torque fluctuation suppressing device, and more particularly to a torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input. The present invention also relates to a torque converter and a power transmission device including a torque fluctuation suppressing device.

  For example, a clutch device including a damper device and a torque converter are provided between an automobile engine and a transmission. Further, the torque converter is provided with a lockup device for mechanically transmitting torque at a predetermined rotational speed or more in order to reduce fuel consumption.

  Generally, the lock-up device has a clutch portion and a damper having a plurality of torsion springs. The clutch portion has a piston with a friction member that is pressed against the front cover by the action of hydraulic pressure. In the lock-up-on state, torque is transmitted from the front cover to the piston via the friction member, and further transmitted to the output side member via the plurality of torsion springs.

  In such a lock-up device, torque fluctuations (rotational speed fluctuations) are suppressed by a damper having a plurality of torsion springs.

  Further, in the lockup device disclosed in Patent Document 1, torque fluctuations are suppressed by providing a dynamic damper device including an inertia member. The dynamic damper device of Patent Document 1 is mounted on a plate that supports a torsion spring, a pair of inertia rings that are rotatable relative to the plate, and a plurality of coil springs provided between the plate and the inertia ring. And have.

Japanese Patent Laying-Open No. 2015-094424

  In the conventional dynamic damper device including Patent Document 1, the peak of torque fluctuation in a predetermined rotation speed range can be suppressed. However, when the engine specifications change, the rotational speed range in which the peak of torque fluctuations changes accordingly. For this reason, it is necessary to change the inertial amount of inertia and the spring constant of the coil spring in accordance with changes in the engine specifications and the like, which may be difficult to cope with.

  An object of the present invention is to enable a peak of torque fluctuation to be suppressed in a relatively wide rotational speed range in an apparatus for suppressing torque fluctuation of a rotating member.

  (1) A torque fluctuation suppressing device according to the present invention is a device for suppressing torque fluctuation of a rotating body to which torque is input, and includes a mass body, a centrifuge, and a cam mechanism. The mass body is arranged side by side with the rotating body in the axial direction, is rotatable with the rotating body, and is disposed so as to be relatively rotatable with respect to the rotating body. The centrifuge is arranged to receive a centrifugal force generated by the rotation of the rotating body and the mass body. The cam mechanism has a cam and a cam follower that moves along the cam. When the cam mechanism receives a centrifugal force acting on the centrifuge, a relative displacement in the rotation direction occurs between the rotating body and the mass body. The centrifugal force is converted into a circumferential force in a direction in which the relative displacement is reduced.

  The cam is provided in the centrifuge. The cam follower is provided on either the rotating body or the mass body. The centrifuge is formed to extend in the rotation direction, and has a guide portion that abuts against members adjacent to both ends in the rotation direction to guide the movement of the centrifuge. When the relative displacement in the rotation direction occurs between the rotating body and the mass body, the guide portion of the centrifuge is adjacent to the contact point between the cam and the cam follower at least on the opposite side across the center of gravity of the centrifuge. Abuts the member.

  In this device, when torque is input to the rotating body, the rotating body and the mass body rotate. When there is no change in the torque input to the rotating body, there is no relative displacement in the rotating direction between the rotating body and the mass body, and the rotor rotates synchronously. On the other hand, when there is a fluctuation in the input torque, the mass body is arranged so as to be relatively rotatable with respect to the rotating body. This displacement may be expressed as “rotational phase difference”).

  Here, when the rotating body and the mass body rotate, the centrifuge receives a centrifugal force. When a relative displacement occurs between the rotating body and the mass body, the cam mechanism converts the centrifugal force acting on the centrifuge into a circumferential force, and this circumferential force causes the rotation between the rotating body and the mass body. It operates to reduce the relative displacement of. Torque fluctuation is suppressed by the operation of the cam mechanism.

  Here, since the centrifugal force acting on the centrifuge is used as a force for suppressing the torque fluctuation, the characteristic for suppressing the torque fluctuation changes according to the rotational speed of the rotating body. Further, for example, the characteristics for suppressing torque fluctuation can be appropriately set depending on the shape of the cam and the like, and the peak of torque fluctuation in a wider rotational speed range can be suppressed.

  Also, here, when a relative displacement in the rotational direction occurs between the rotating body and the mass body and the cam mechanism is activated, the guide portion of the centrifuge is a contact point between the cam and the cam follower with the center of gravity of the centrifuge interposed therebetween. And at least a position opposite to the adjacent member. For this reason, in a centrifuge, it can suppress that the rotational moment which made the end of the rotation direction a fulcrum arises. Therefore, the centrifuge moves smoothly, and the configuration of the guide portion can be simplified.

  (2) Preferably, the mass body has a first inertia ring and a second inertia ring arranged to face each other with the rotating body interposed therebetween.

  Here, since the inertia rings are arranged on both sides in the axial direction of the rotating body, the radial dimension of the device can be suppressed and the inertia amount can be increased, which is effective in suppressing torque fluctuation.

  (3) Preferably, the mass body further includes a pin that passes through the rotating body in the axial direction and connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. Preferably, the centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin. The cam follower is a cylindrical roller having a hole through which a pin penetrates in the axial direction. In addition, the cam is formed in the centrifuge and contacts the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body.

  Here, the cam follower is mounted using a pin connecting the first inertia ring and the second inertia ring. This simplifies the configuration of the cam mechanism.

  (4) Preferably, a rotary body has a projection part in an outer peripheral surface, and a centrifuge has the 1st member and 2nd member arrange | positioned so that a projection part may be pinched | interposed in an axial direction. And the guide part of a centrifuge connects the 1st member and the 2nd member, and contact | abuts to the both sides | surfaces of the protrusion part of a rotary body.

  (5) Preferably, the guide portion is a pair of rollers that are rotatably supported at both ends in the circumferential direction of the centrifuge and roll on both side surfaces of the protrusion of the rotating body.

  If the centrifuge is configured to generate a rotational moment with one end in the rotation direction as a fulcrum, in order to move the centrifuge smoothly, a pair of guide portions are provided, for example, on the inner peripheral side and the outer peripheral side. (2 pairs of rollers in total) must be provided.

  However, in the present invention, as described above, in the centrifuge, since the rotational moment with one end in the rotational direction as a fulcrum is suppressed, even if the guide portion is configured by only a pair of rollers, The centrifuge can be moved smoothly.

  (6) Preferably, the mass body further includes a pin that passes through the rotating body in the axial direction and connects the first inertia ring and the second inertia ring so as not to be relatively rotatable. Preferably, the centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the inner peripheral side of the pin. The cam follower is a cylindrical roller having a hole through which a pin penetrates in the axial direction. In addition, the cam is formed in the centrifuge and contacts the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body.

  (7) Preferably, the rotating body has a protruding portion that protrudes toward the inner peripheral side, and the centrifuge has a first member and a second member that are arranged so as to sandwich the protruding portion in the axial direction. And the guide part of a centrifuge connects the 1st member and the 2nd member, and contact | abuts to the both sides | surfaces of the protrusion part of a rotary body.

  (8) Preferably, the mass body is formed in a continuous annular shape.

  (7) The torque converter according to the present invention is disposed between the engine and the transmission. The torque converter includes an input-side rotating body that receives torque from the engine, an output-side rotating body that outputs torque to the transmission, and a damper that is disposed between the input-side rotating body and the turbine. Any of the torque fluctuation suppression devices.

  (8) The power transmission device according to the present invention includes a flywheel, a clutch device, and any one of the torque fluctuation suppressing devices described above. The flywheel includes a first inertial body that rotates about a rotation axis, a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body, and a first inertial body and a second inertial body. And a damper disposed therebetween. The clutch device is provided on the second inertial body of the flywheel.

  In the present invention as described above, in the apparatus for suppressing the torque fluctuation of the rotating member, the peak of the torque fluctuation can be suppressed in a relatively wide rotational speed range. Moreover, in this invention, a centrifuge can be moved smoothly with the structure of a simple guide part.

The schematic diagram of the torque converter by a 1st embodiment of the present invention. FIG. 2 is a partial front view of the output side rotating body and the torque fluctuation suppressing device of FIG. 1. FIG. 3 is an arrow A view of FIG. 2. The figure for demonstrating the action | operation of a cam mechanism. The figure for demonstrating the action | operation of a cam mechanism. The characteristic view which shows the relationship between a rotation speed and a torque fluctuation. The figure equivalent to FIG. 2 of 2nd Embodiment of this invention. The arrow B figure of FIG. The schematic diagram which shows the application example 1 of this invention. The schematic diagram which shows the application example 2 of this invention. The schematic diagram which shows the application example 3 of this invention. The schematic diagram which shows the application example 4 of this invention. The schematic diagram which shows the application example 5 of this invention. The schematic diagram which shows the application example 6 of this invention. The schematic diagram which shows the application example 7 of this invention. The schematic diagram which shows the application example 8 of this invention. The schematic diagram which shows the application example 9 of this invention.

-First embodiment-
FIG. 1 is a schematic diagram when the torque fluctuation suppressing device according to the first embodiment of the present invention is mounted on a lock-up device of a torque converter. In FIG. 1, OO is the rotational axis of the torque converter.

[overall structure]
The torque converter 1 includes a front cover 2, a torque converter main body 3, a lockup device 4, and an output hub 5. Torque is input to the front cover 2 from the engine. The torque converter main body 3 includes an impeller 7 connected to the front cover 2, a turbine 8, and a stator (not shown). The turbine 8 is connected to the output hub 5, and an input shaft (not shown) of the transmission can be engaged with the inner peripheral portion of the output hub 5 by a spline.

[Lock-up device 4]
The lock-up device 4 has a clutch part, a piston that is operated by hydraulic pressure, and the like, and can take a lock-up on state and a lock-up off state. In the lock-up on state, the torque input to the front cover 2 is transmitted to the output hub 5 via the lock-up device 4 without passing through the torque converter body 3. On the other hand, in the lock-up off state, torque input to the front cover 2 is transmitted to the output hub 5 via the torque converter body 3.

  The lockup device 4 includes an input-side rotator 11, an output-side rotator 12, a damper 13, and a torque fluctuation suppressing device 14.

  The input-side rotator 11 includes a piston that is movable in the axial direction, and has a friction member 16 on a side surface on the front cover 2 side. When the friction member 16 is pressed against the front cover 2, torque is transmitted from the front cover 2 to the input side rotating body 11.

  The output-side rotator 12 is disposed so as to face the input-side rotator 11 in the axial direction, and is rotatable relative to the input-side rotator 11. The output side rotating body 12 is connected to the output hub 5.

  The damper 13 is disposed between the input side rotating body 11 and the output side rotating body 12. The damper 13 has a plurality of torsion springs, and elastically connects the input side rotating body 11 and the output side rotating body 12 in the rotation direction. The damper 13 transmits torque from the input-side rotator 11 to the output-side rotator 12, and absorbs and attenuates torque fluctuations.

[Torque fluctuation suppressing device 14]
FIG. 2 is a front view of the output side rotating body 12 and the torque fluctuation suppressing device 14. 2 shows a part of the output-side rotator 12 and the torque fluctuation suppressing device 14, but as a whole, the portions shown in FIG. 2 are provided at equiangular intervals at four locations in the circumferential direction. ing. FIG. 3 is a view seen from the direction A in FIG.

  The torque fluctuation suppressing device 14 includes a first inertia ring 201 and a second inertia ring 202 that constitute the mass body 20, four centrifuges 21, and four cam mechanisms 22.

  The first and second inertia rings 201 and 202 are plates each having a predetermined thickness formed in a continuous annular shape. As shown in FIG. 3, the output-side rotator 12 sandwiches the output-side rotator 12. Are arranged with a predetermined gap on both sides in the axial direction. That is, the output-side rotating body 12 and the first and second inertia rings 201 and 202 are arranged side by side in the axial direction. The first and second inertia rings 201 and 202 have the same rotation axis as that of the output-side rotator 12, can rotate together with the output-side rotator 12, and can rotate relative to the output-side rotator 12. It is.

  The first and second inertia rings 201 and 202 are formed with holes 201a and 202a penetrating in the axial direction. And the 1st inertia ring 201 and the 2nd inertia ring 202 are being fixed by the rivet 24 which penetrates those holes 201a and 202a. Therefore, the first inertia ring 201 cannot move in the axial direction, the radial direction, and the rotation direction with respect to the second inertia ring 202.

  The output-side rotator 12 is formed in a disc shape, and the inner peripheral portion is connected to the output hub 5 as described above. Four protrusions 121 having a predetermined width are formed in the circumferential direction on the outer peripheral portion of the output-side rotator 12. The protrusion 121 is inserted between the first inertia ring 201 and the second inertia ring 202 in the axial direction. The outer peripheral end of the protruding portion 121 is formed so as to be positioned at a substantially middle portion between the inner diameter and the outer diameter of the first and second inertia rings 201 and 202. More specifically, as will be described later, the roller 30 constituting the cam mechanism 22 moves along the cam 31, but the roller 30 does not hit the outer peripheral end surface of the protrusion 121 during the movement of the roller 30. The outer diameter of the protrusion 121 is set.

  The centrifuge 21 has a first member 211 and a second member 212 extending in the rotation direction. The first and second members 211 and 212 have the same shape, and are arranged in the axial direction via a predetermined gap. The first and second members 211 and 212 sandwich the protrusion 121 of the output-side rotator 12 on the inner peripheral side of the rivet 24 between the axial directions of the first inertia ring 201 and the second inertia ring 202. Are arranged. The centrifuge 21 rotates with the output-side rotator 12 and is movable in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 12.

  More specifically, one first guide roller 26a and one second guide roller 26b (guide portion) are disposed at both ends in the longitudinal direction (rotation direction) of the first and second members 211 and 212, respectively. . The first and second guide rollers 26a and 26b are rotatably mounted via bushes 28 around pins 27 supported at both ends of the first and second members 211 and 212. The outer peripheral surface of the first roller 26a can be brought into contact with one side surface 121a of the protrusion 121 and can be rolled, and the outer peripheral surface of the second roller 26b can be brought into contact with the other side surface 121b of the protrusion 121 and rolled. Is possible.

  The first and second members 211 and 212 of the centrifuge 21 are formed in an arc shape in which the outer peripheral surfaces 211a and 212a are recessed toward the inner peripheral side, and as will be described later, these outer peripheral surfaces 211a and 212a, 212 a functions as the cam 31.

  The cam mechanism 22 includes a cylindrical roller 30 as a cam follower and cams 31 that are outer peripheral surfaces 211 a and 212 a of the first and second members 211 and 212. The roller 30 is fitted on the outer periphery of the trunk portion of the rivet 24. That is, the roller 30 is supported by the rivet 24. The roller 30 is preferably mounted so as to be rotatable with respect to the rivet 24, but may not be rotatable. The cam 31 is an arcuate surface with which the roller 30 abuts. When the output-side rotating body 12 and the first and second inertia rings 201 and 202 are relatively rotated within a predetermined angular range, the roller 30 It moves along the cam 31.

  As will be described in detail later, when a rotational phase difference is generated between the output-side rotating body 12 and the first and second inertia rings 201 and 202 due to contact between the roller 30 and the cam 31, it occurs in the centrifuge 21. The centrifugal force is converted into a circumferential force that reduces the rotational phase difference.

[Operation of cam mechanism 22]
The operation of the cam mechanism 22 (torque fluctuation suppression) will be described with reference to FIGS. In the following description, the first and second inertia rings 201 and 202 may be simply referred to as “inertia ring 20”.

  When the lockup is on, the torque transmitted to the front cover 2 is transmitted to the output-side rotator 12 via the input-side rotator 11 and the damper 13.

  When there is no torque fluctuation during torque transmission, the output side rotating body 12 and the inertia ring 20 rotate in the state shown in FIG. In this state, the roller 30 of the cam mechanism 22 is in contact with the innermost position (the center position in the circumferential direction) of the cam 31, and the rotational phase difference between the output-side rotating body 12 and the inertia ring 20 is “0”. It is.

  As described above, the relative displacement amount in the rotational direction between the output-side rotator 12 and the inertia ring 20 is referred to as a “rotational phase difference”. In FIG. 2, FIG. 4 and FIG. The deviation between the center position of the centrifuge 21 and the cam 31 in the circumferential direction and the center position of the roller 30 is shown.

  Here, if torque fluctuation exists during torque transmission, a rotational phase difference ± θ is generated between the output side rotating body 12 and the inertia ring 20 as shown in FIGS. 4 and 5. FIG. 4 shows a case where a rotational phase difference + θ occurs on the + R side, and FIG. 5 shows a case where a rotational phase difference −θ occurs on the −R side.

  As shown in FIG. 4, when a rotational phase difference + θ occurs between the output-side rotator 12 and the inertia ring 20, the roller 30 of the cam mechanism 22 moves relatively along the cam 31 to the left side in FIG. 4. Move to. At this time, since centrifugal force is applied to the centrifuge 21, the reaction force received from the roller 30 by the cam 31 formed on the centrifuge 21 is in the direction and magnitude of P0 in FIG. The reaction force P0 generates a first component force P1 in the circumferential direction and a second component force P2 in a direction that moves the centrifuge 21 toward the inner periphery.

  The first component force P1 is a force that moves the output side rotating body 12 in the left direction in FIG. 4 via the cam mechanism 22 and the centrifuge 21. That is, a force in the direction of reducing the rotational phase difference between the output side rotating body 12 and the inertia ring 20 acts on the output side rotating body 12. Moreover, the centrifuge 21 is moved to the inner peripheral side against the centrifugal force by the second component force P2.

  FIG. 5 shows a case where a rotational phase difference −θ is generated between the output-side rotator 12 and the inertia ring 20. The moving direction of the roller 30 of the cam mechanism 22, the reaction force P 0, and the first component force P 1. The cam mechanism 22 operates in the same manner except that the direction of the second component force P2 is different from that in FIG.

  As described above, when a rotational phase difference is generated between the output-side rotating body 12 and the inertia ring 20 due to torque fluctuation, the output-side rotating body 12 is caused by the centrifugal force acting on the centrifuge 21 and the action of the cam mechanism 22. , A force (first component force P1) in a direction to reduce the rotational phase difference between the two is received. This force suppresses torque fluctuations.

  The force that suppresses the torque fluctuation described above varies depending on the centrifugal force, that is, the rotational speed of the output-side rotator 12, and also varies depending on the rotational phase difference and the shape of the cam 31. Therefore, by setting the shape of the cam 31 as appropriate, the characteristics of the torque fluctuation suppressing device 14 can be optimized according to engine specifications and the like.

  For example, the shape of the cam 31 can be made such that the first component force P1 changes linearly according to the rotational phase difference in the state where the same centrifugal force is acting. In addition, the shape of the cam 31 can be a shape in which the first component force P1 changes nonlinearly according to the rotational phase difference.

[Example of characteristics]
FIG. 6 is a diagram illustrating an example of torque fluctuation suppression characteristics. The horizontal axis represents the rotational speed, and the vertical axis represents the torque fluctuation (rotational speed fluctuation). The characteristic Q1 is a case where a device for suppressing torque fluctuation is not provided, the characteristic Q2 is a case where a conventional dynamic damper device is provided, and the characteristic Q3 is a case where the torque fluctuation suppressing device 14 of the present embodiment is provided. Show.

  As is apparent from FIG. 6, in the device (characteristic Q2) provided with the conventional dynamic damper device, it is possible to suppress the torque fluctuation only in a specific rotational speed range. On the other hand, in the present embodiment (characteristic Q3), torque fluctuation can be suppressed in all the rotational speed ranges.

[Operation of centrifuge 21]
For example, as shown in FIG. 4, when a rotational phase difference is generated between the output side rotating body 12 and the inertia ring 20, the centrifuge 21 has a force P 0 from the inertia ring 20 at the contact C 1 with the roller 30. Works. With this force P0, the first guide roller 26a attached to the centrifuge 21 and one side surface 121a of the projection 121 come into contact with each other at the contact C2, and the second guide roller 26b and the other side surface 121b of the projection 121 are in contact with each other. Abuts at the contact C3. That is, as shown in FIG. 4, when a rotational phase difference of + θ occurs between the output-side rotator 12 and the inertia ring 20, the force acts on the contact C3 with the center of gravity G of the centrifuge 21 in between. A force acts on at least the contact points C1 and C2 on both sides thereof. In this case, with the contact C2 as a fulcrum, a moment acts clockwise on the centrifuge 21 due to the centrifugal force W acting on the center of gravity G, and a counterclockwise moment acts on the contact C1 due to the force P0. For this reason, a large rotational moment does not act on the centrifuge 21 only on one side. Therefore, the centrifuge 21 can be prevented from tilting, and the centrifuge 21 can be smoothly moved in the radial direction only by the two guide rollers 26a and 26b.

-Second Embodiment-
FIG. 7 shows a second embodiment of the present invention. FIG. 7 is a view corresponding to FIG. 2 of the first embodiment, and in the second embodiment as well, the configuration shown in FIG. 7 is provided at four equiangular intervals in the circumferential direction as described above. ing. FIG. 8 is a view seen from the direction B of FIG.

  The torque fluctuation suppression device 14 ′ of the second embodiment includes a first inertia ring 201 ′ and a second inertia ring 202 ′ that constitute the mass body 20 ′, four centrifuges 21 ′, and four cam mechanisms 22. 'And have.

  The first and second inertia rings 201 ′ and 202 ′ are plates each having a predetermined thickness formed in a continuous annular shape. As shown in FIG. 8, the output side rotating body 12 ′ is sandwiched between the output side and the output side. The rotating body 12 ′ is disposed with a predetermined gap on both sides in the axial direction. The first and second inertia rings 201 ′ and 202 ′ have the same rotation axis as that of the output side rotating body 12 ′, can rotate together with the output side rotating body 12 ′, and are connected to the output side rotating body 12 ′. Relative rotation is possible.

  As in the first embodiment, the first and second inertia rings 201 ′ and 202 ′ are fixed by a rivet 24 ′ and cannot move in the axial direction, the radial direction, and the rotational direction.

  The output side rotating body 12 ′ is formed in a disc shape and is connected to the output hub 5. Four openings 120 ′ are formed on the outer peripheral portion of the output-side rotator 12 ′, and a protrusion 121 ′ protruding to the inner peripheral side is formed in the opening 120 ′. Further, the output-side rotator 12 'is formed with an arc groove 122' extending in the circumferential direction. A rivet 24 'passes through the arc groove 122'. Accordingly, the first and second inertia rings 201 ′ and 202 ′ can be rotated relative to the output-side rotating body 12 ′ by an angle that allows the barrel portion of the rivet 24 to move within the arc groove 122 ′. In other words, a stopper mechanism that restricts relative rotation between the first and second inertia rings 201 ′ and 202 ′ and the output side rotating body 12 ′ is configured by the body portion of the rivet 24 ′ and the circular groove 122 ′. .

  The centrifuge 21 'has a first member 211' and a second member 212 'extending in the rotation direction. The first and second members 211 ′ and 212 ′ have the same shape and are arranged in the axial direction with a predetermined gap. The first and second members 211 ′ and 212 ′ are arranged between the first inertia ring 201 ′ and the second inertia ring 202 ′ on the inner peripheral side of the rivet 24 ′ and the output side rotating body 12 ′. It arrange | positions so that protrusion part 121 'may be pinched | interposed. The centrifuge 21 'rotates together with the output-side rotator 12' and is movable in the radial direction by the centrifugal force generated by the rotation of the output-side rotator 12 '.

  More specifically, a first guide roller 26a ′ and a second guide roller 26b ′ (guide portion) are provided at both ends in the longitudinal direction (rotation direction) of the first and second members 211 ′ and 212 ′, respectively. Is arranged. The first and second guide rollers 26a 'and 26b' are rotatably mounted around the pins 27 'supported at both ends of the first and second members 211' and 212 '. Then, the outer peripheral surface of the first roller 26a 'can abut on one side surface 121a' of the protrusion 121 'and roll, and the outer peripheral surface of the second roller 26b' can be the other side surface 121b 'of the protrusion 121'. It is possible to roll in contact with. Although details of the configuration for supporting the centrifuge 21 ′ are omitted, for example, it is conceivable to contact the outer periphery (not shown) of the opening 120 ′.

  In the same manner as described above, the outer peripheral surfaces 211a 'and 212a' of the centrifuge 21 'are formed in a circular arc shape recessed toward the inner peripheral side and function as the cam 31'.

  The configuration of the cam mechanism 22 'is basically the same as that of the first embodiment. That is, it is composed of a cylindrical roller 30 ′ as a cam follower and a cam 31 ′ that is the outer peripheral surfaces 211 a ′ and 212 a ′ of the centrifuge 21 ′. In the second embodiment, the roller 30 ′ includes a first roller 311 ′ and a second roller 312 ′. The first roller 311 'is disposed between the first inertia ring 201' and the output side rotating body 12 'in the axial direction, and rolls on the outer peripheral surface 211a' of the first member 211 '. The second roller 312 'is disposed between the second inertia ring 202' and the output-side rotating body 12 'in the axial direction, and rolls on the outer peripheral surface 212a' of the second member 212 '.

  Since the operation of the cam mechanism 22 'is the same as that of the first embodiment, it is omitted here.

[Other Embodiments]
The present invention is not limited to the above-described embodiments, and various changes or modifications can be made without departing from the scope of the present invention.

  (A) In the said embodiment, although inertia ring was comprised with the continuous annular member, you may arrange | position the some inertia body divided | segmented along with the circumferential direction. In this case, in order to hold a plurality of inertia bodies, it is necessary to provide a holding member such as an annular holding ring on the outer peripheral side of the inertia body.

  (B) In the above embodiment, the centrifuge is arranged on the output side rotator and the cam follower is provided on the inertia ring. Conversely, the centrifuge may be arranged on the inertia ring and the cam follower is provided on the output side rotator. Good.

  (C) In the above-described embodiment, the guide roller is disposed as the guide portion. However, another member that reduces friction such as a resin race or a sheet may be disposed.

[Application example]
When the torque fluctuation suppressing device as described above is applied to a torque converter or another power transmission device, various arrangements are possible. Below, a specific application example is demonstrated using the schematic diagram of a torque converter or another power transmission device.

  (1) FIG. 9 is a diagram schematically showing a torque converter, which includes an input-side rotating body 41, an output-side rotating body 42, and a damper provided between both rotating bodies 41, 42. 43. The input side rotating body 41 includes members such as a front cover, a drive plate, and a piston. The output side rotating body 42 includes a driven plate and a turbine hub. The damper 43 includes a plurality of torsion springs.

  In the example shown in FIG. 9, a centrifuge is provided in any of the rotating members that constitute the input-side rotator 41, and a cam mechanism 44 that operates using the centrifugal force acting on the centrifuge is provided. It has been. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

  (2) The torque converter shown in FIG. 10 is provided with a centrifuge in any one of the rotating members constituting the output-side rotator 42, and is a cam mechanism that operates using centrifugal force acting on the centrifuge. 44 is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

  (3) The torque converter shown in FIG. 11 has another damper 45 and an intermediate member 46 provided between the two dampers 43, 45 in addition to the configurations shown in FIGS. doing. The intermediate member 46 is relatively rotatable with the input side rotating body 41 and the output side rotating body 42, and causes the two dampers 43 and 45 to act in series.

  In the example shown in FIG. 11, the intermediate member 46 is provided with a centrifuge, and a cam mechanism 44 that operates by utilizing a centrifugal force acting on the centrifuge is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

  (4) The torque converter shown in FIG. 12 has a float member 47. The float member 47 is a member for supporting the torsion spring constituting the damper 43, and is formed, for example, in an annular shape so as to cover the outer periphery and at least one side surface of the torsion spring. The float member 47 is relatively rotatable with the input-side rotator 41 and the output-side rotator 42, and rotates around the damper 43 by friction with the torsion spring of the damper 43. That is, the float member 47 also rotates.

  In the example shown in FIG. 12, the float member 47 is provided with a centrifuge 48, and a cam mechanism 44 that operates using a centrifugal force acting on the centrifuge 48 is provided. About the cam mechanism 44, the structure similar to the structure shown by the said each embodiment is applicable.

  (5) FIG. 13 is a schematic diagram of a power transmission device having a flywheel 50 having two inertia bodies 51, 52 and a clutch device 54. In other words, the flywheel 50 disposed between the engine and the clutch device 54 includes a first inertial body 51, a second inertial body 52 disposed so as to be rotatable relative to the first inertial body 51, and two inertial bodies. And a damper 53 disposed between 51 and 52. The second inertia body 52 also includes a clutch cover that constitutes the clutch device 54.

  In the example shown in FIG. 13, a centrifuge is provided in one of the rotating members that constitute the second inertial body 52, and a cam mechanism 55 that operates using a centrifugal force acting on the centrifuge is provided. ing. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

  (6) FIG. 14 is an example in which a centrifuge is provided in the first inertial body 51 in the same power transmission device as that in FIG. A cam mechanism 55 that operates using centrifugal force acting on the centrifuge is provided. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

  (7) In addition to the configuration shown in FIGS. 13 and 14, the power transmission device shown in FIG. 15 includes another damper 56 and an intermediate member 57 provided between the two dampers 53, 56. Have. The intermediate member 57 is rotatable relative to the first inertial body 51 and the second inertial body 52.

  In the example shown in FIG. 15, the intermediate member 57 is provided with a centrifuge 58, and a cam mechanism 55 that operates by utilizing a centrifugal force acting on the centrifuge 58 is provided. For the cam mechanism 55, the same configuration as that shown in each of the above embodiments can be applied.

  (8) FIG. 16 is a schematic diagram of a power transmission device in which a clutch device is provided on one flywheel. The first inertia body 61 in FIG. 16 includes one flywheel and a clutch cover of the clutch device 62. In this example, a centrifuge is provided in any of the rotating members constituting the first inertial body 61, and a cam mechanism 64 that operates by utilizing a centrifugal force acting on the centrifuge is provided. About the cam mechanism 64, the structure similar to the structure shown by the said each embodiment is applicable.

  (9) FIG. 17 is an example in which a centrifuge 65 is provided on the output side of the clutch device 62 in the same power transmission device as FIG. A cam mechanism 64 that operates by utilizing the centrifugal force acting on the centrifuge 65 is provided. About the cam mechanism 64, the structure similar to the structure shown by the said each embodiment is applicable.

  (10) Although not shown in the drawings, the torque fluctuation suppressing device of the present invention may be disposed on any of the rotating members constituting the transmission, and further, the shaft (propeller shaft or drive) on the output side of the transmission (Shaft).

  (11) As another application example, the torque fluctuation suppressing device of the present invention may be further applied to a conventionally known dynamic damper device or a power transmission device provided with a pendulum type damper device.

DESCRIPTION OF SYMBOLS 1 Torque converter 11 Input side rotary body 12 Output side rotary body 121 Protrusion part 14 Torque fluctuation suppression apparatus 20, 201, 202 Inertia ring (mass body)
21 Centrifuge 211 First member 212 Second member 22 Cam mechanism 26a, 26b Guide roller 30 Roller (cam follower)
31 cams

Claims (10)

A torque fluctuation suppressing device for suppressing torque fluctuation of a rotating body to which torque is input,
A mass body that is arranged side by side with the rotating body, is rotatable with the rotating body, and is relatively rotatable with respect to the rotating body;
A centrifuge arranged to receive a centrifugal force due to rotation of the rotating body and the mass body;
A cam and a cam follower that moves along the cam, and receives a centrifugal force acting on the centrifuge, and when a relative displacement in the rotational direction occurs between the rotating body and the mass body, A cam mechanism for converting the centrifugal force into a circumferential force in a direction in which the relative displacement is reduced;
With
The cam is provided on the centrifuge;
The cam follower is provided on either the rotating body or the mass body,
The centrifuge is formed to extend in the rotation direction, and has a guide portion that contacts a member adjacent to both ends in the rotation direction to guide the movement of the centrifuge,
When relative displacement in the rotational direction occurs between the rotating body and the mass body, the guide portion of the centrifuge is positioned opposite to the contact point of the cam and the cam follower across the center of gravity of the centrifuge. In contact with the adjacent member,
Torque fluctuation suppression device.   2. The torque fluctuation suppressing device according to claim 1, wherein the mass body includes a first inertia ring and a second inertia ring that are arranged to face each other with the rotating body interposed therebetween. The mass body further includes a pin that passes through the rotating body in the axial direction and connects the first inertia ring and the second inertia ring so as not to be relatively rotatable,
The centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the outer peripheral portion of the rotating body and on the inner peripheral side of the pin.
The cam follower is a cylindrical roller having a hole through which the pin penetrates in the axial direction.
The cam is formed on the centrifuge and abuts on the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body. ,
The torque fluctuation suppressing device according to claim 2. The rotating body has a protrusion on the outer peripheral surface,
The centrifuge has a first member and a second member arranged so as to sandwich the protrusion in the axial direction,
The guide portion of the centrifuge connects the first member and the second member and abuts on both side surfaces of the protrusion of the rotating body.
The torque fluctuation suppressing device according to any one of claims 1 to 3.   The torque variation according to claim 4, wherein the guide portion is a pair of rollers that are rotatably supported at both circumferential ends of the centrifuge and roll on both side surfaces of the protrusion of the rotating body. Suppression device. The mass body further includes a pin that passes through the rotating body in the axial direction and connects the first inertia ring and the second inertia ring so as not to be relatively rotatable,
The centrifuge is arranged between the first inertia ring and the second inertia ring in the axial direction on the inner peripheral side of the pin,
The cam follower is a cylindrical roller having a hole through which the pin penetrates in the axial direction.
The cam is formed on the centrifuge and abuts on the cam follower, and has a shape such that the circumferential force changes according to the relative displacement amount in the rotational direction between the rotating body and the mass body. ,
The torque fluctuation suppressing device according to claim 2. The rotating body has a protruding portion that protrudes to the inner peripheral side,
The centrifuge has a first member and a second member arranged so as to sandwich the protrusion in the axial direction,
The guide portion of the centrifuge connects the first member and the second member and abuts on both side surfaces of the protrusion of the rotating body.
The torque fluctuation suppressing device according to claim 6.   The torque fluctuation suppressing device according to any one of claims 1 to 7, wherein the mass body is formed in a continuous annular shape. A torque converter disposed between the engine and the transmission,
An input-side rotating body to which torque from the engine is input;
An output-side rotating body that outputs torque to the transmission;
A damper disposed between the input-side rotor and the turbine;
A torque fluctuation suppressing device according to any one of claims 1 to 8,
Torque converter with A first inertial body that rotates about a rotation axis; a second inertial body that rotates about the rotation axis and is rotatable relative to the first inertial body; and the first inertial body and the second inertial body. A flywheel having a damper disposed therebetween,
A clutch device provided in the second inertial body of the flywheel;
A torque fluctuation suppressing device according to any one of claims 1 to 8,
Power transmission device with

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